Gas pumping



March 4, 1941. .1. J. WYDLER GAS PUMPING Filed NOV. 12, 1938 QM my amd,.f w

i294. if??? if@ VOLUME lZ INVENTOR JOHANN u. wYDLER BYZ Z1 d ATTORNEYVOLUME Patented Mar. 4, 1941 PATENT OFFICE GAS PUBIPING Johann J.Wydier, Westfield, N. J., assigner. by

mesne assignments, to Cities Service Oil C ompany, New York, N. Y., acorporation of Penn- Sylvania Application November 12, 1938, Serial No.240,015

20 Claims.

This invention relates to gas pumping, and has particular reference toimprovements in method and apparatus for utilizing the potential energyof hot gases under low pressure for producing iiow of cold gases.

A particular object of the invention is to provide a novel way forutilizing the potential energy which is available in the hot wasteexhaust gases discharged from an internal combustion engine.

Another object is that of providing method and means for eiiicientlyconverting the pressure and temperature energy of one hot body or streamof gas into kinetic and pressure energy of other cold gas bodies.

A particular feature of the invention resides in a novel form ofapparatus which may be broadly termed a gas displacement and breatherpump. Essentially this apparatus consists of a wall-enclosed vesselhaving valved gas inlet ports at both top and bottom and having a bottomgas outlet and a cooling element. The pump is so arranged and operatedthat hot engine exhaust gases, for example, may be introduced underpressure into the top of the vessel originally lled with air or coldgases, thereby imparting pressure and kinetic energy to the cold gaseswhich are displaced and forced out of the bottom of the pump by the hotgases, while the hot gases are expended to atmospheric pressure; afterwhich the hot gases are cooled as by recuperative heat transfer andundergo a shrinkage in volume which is sufficient to allow the breathinginto the bottom of the vessel of cold air or gas flowing from someexternal source. The masses of cold gases put into motion under denitepressure differentials during discharge and suction intake periodsafford means to transform the energy lost by the exhaust gases duringthe discharge and intake periods into useful mechanical work indirectly,as by means of a turbine wheel.

In so doing, the operating cycle may be actually continued into theranges below atmospheric pressure with all its beneficial consequencesfor utilizing the lower heat ranges. Such procedure of course wouldalways be impractical with any mechanical piston apparatus.

The exhaust loss which usually is involved in standard operation ofinternal combustion engines consists mainly vof two major portions. Therst portion is represented by the waste of potential pressure energywhich discharges the cylinder content to the outside at a high rate lofspeed Without doing any mechanically useful work. The other portion isthe great amount of intrinsic heat still contained in the exhaust gasesafter they have reached pressure balance With the outside atmosphere,and which in such form represent a great amount of useless anddegenerated heat energy.

It is therefore a feature of the invention to provide a displacementandA breather type pump which makes it possible to utilize both of theseportions of the exhaust energy of an internal combustion engine.

Another object of the invention is to provide a method and apparatus forcompressing and pumping air or other gas without the use of expensivemechanical means. Such air may be used for supercharging an internalcombustion engine.

Further objects and advantages of the present invention will be apparentfrom the following description taken in connection with the accompanyingdrawing, in which:

Fig, 1 is a pressure-volume diagram illustrating the Variation inabsolute pressure combined with the movement of the gas fronts inside adisplacement and breather type pump over one complete cycle;

Fig. 2 shows diagrammatlcally the change in gas weights occurring duringone complete cycle;

Fig. 3 is a diagrammatic view showing the arrangement of the coolingapparatus and valves at the period 2U (Fig. 1) of the cycle of the pump;Fig'. 4 is a diagrammatic view showing the hot gas inlet valve openduring the admission period 20-22-24 of the cycle;

Fig. 5 is a diagrammatic View showing the relative positions of thecooling apparatus and valves at the end 24 of the admission period20--22-24.

Fig. 6 is a diagrammatic View showing the closed position of an inletvalve for the cold air and the open position of an outlet valve for the-cold exhaust during the discharge and expansion period n n- 26;

Fig. 7 is a. diagrammatic View showing the re1- ative positions of thecooling apparatus and Valves at the end 26 of the discharge andexpansion period 2224-26;

Fig, 8v is a diagrammatic view showing the positions of the inlet valvefor the cold air and the outlet valve for the cold exhaust during thecondensation period 26--28;

Fig. 9 is a diagrammatic view showing the posiof the cooling apparatusand valves: during the cooling period 28-29-3U;

Fig. 10 is an end vertical sectional view of a preferred design of pumpshowing the cooling apparatus and valves;

Fig. 11 is aside vertical sectional view of the pump of Fig. 10, withparts shown in elevation.

Fig. 1 displays the PV diagram of the cycle of a pump 32 (Fig. 10)having a valved gas inlet 36 I at its top which may be directlyconnected to the exhaust manifold 48 of an internal combustion engine(not shown), and preferably having sufficient gas storage capacity tohold the exhaust gases discharged from the engine cylinders duringseveral combustion cycles or over a period of several seconds. Followingup the movement of the gas fronts, an indicator card (Fig 1) is obitained which in many respects has the characteristics of a normal cardof a piston engine with*V outside admission. The upper part of the. cardfrom 26 to 26 demonstrates the compression and displacement period ofthe cycle, and the lower part from 26 to 3D demonstrates the cooling andbreathing period.

In Fig. 2 the same numeralsfas in Fig. 1 are used and terminate the samecyclic steps; the ordinates, however, indicate the gas weights involvedinside the pump expressed in multiples of exhaust 'gas weight availablefrom the engine. The values hold true for a definite example with amaximum pressure height of two atmospheres absolute and 1600 F. absoluteexhaust temperature. However, the scope of the invention is not to belimited by these numerical values. l

It has long been known that gases of different temperature, because oftheir different densities, maintain stratiiie'd layers. Such astratification is only nullied ordisturbed if the Whole volume of thehotand cold'gas masses is put into a state of more o-r less violent4motion. If

" the volumetric capacityof the pump container is chosen of suchmagnitude as to be a large multiple of the unit volumes of individualexhaust gas discharges from engine cylinders, the velocity ot influx iseasily reduced as by baille plates so as to prevent violent intermixingbetween the cold air and the hot gases. lSuch stratification is notdisturbed if the hot exhaust gases are acting n ot only as a displacerpushing the cold air which originally occupied the pump out of the pump,but if they are simultaneously compressing'the cold air before or whileany discharging takes place'. The number f exhaust gas discharges whichare lto be dealt with inside of the pump, or the relative volumetriccapacity of the pump, is largely determined by the time required for theefficient cooling' of the hot gases Aduring the later cooling period ofthe cycle.

Analyzing the Acycle diagrams of Figs. 1 and 2 inj'detail, we aredealingwith a cycle either ofbest efciency'or of greatest power capacity,

depending on whether we oper-ate the cycle along the expansion curve'24to 26 or along the broken line 24-2 5-26. In both cases, during theperiod 22-24 the same proportion of cold gascold gas content flows outunder a' changing pressure diierential, dropping from AP to zero.

v1n the second case of greatest capacity, it is lpushed out under theconstant differential AP,

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maintaining its full magnitude to the end at 25. Obviously the cold gascarries with it a maximum amount of energy when discharged under thesecond method. Therst method of discharge 24-26 lrequires a time periodessentially longer than the second method 2li-25. A' correspondingsaving in operating time is utilized conveniently, as explainedhereafter.

Another difference in operation affects the weights of the incoming hotexhaust gases involved. With the irst method admission of hot exhaustgases into the pump terminates at 24. With the second method it `must be continued beyond 21! and maintained up to 25. The rst case presupposesthat admission of exhaust gases is stopped at a point 24 so as to yielda final expanded volume of the exhaust gases at 26 just occupying thetotal pump volume at atmospheric pressure. Thus the admitted exhaustgases return according to this method of operation the maximum ofexpansive working capacity, illustrated by the Aarea 2l-22-24-26.Therefore this case represents the cycle of best efficiency. With thesecond method, the pump is again completely filled with hot gases at 25,which, however, are under higher pressure and therefore represent agreater weight, indicated bythe. ordinate 28-25 in Fig. 2, as against28--26 pertaining to the first method.

-sure and may be subjected immediately to the cooling process in o'rderto make their remaining' intrinsic heat do further work. Under thecooling influence, the exhaust gas shrinks and the pressure is loweredat 28 toy about one-third of an atmosphere. By admittingV fresh air fromthe outside as for example by way of a nozzle and a turbine wheel, thispartial vacuum is gradually filled up along the curve 28-30, with fullatmospheric balance restored at 30. The curve 28-36 may be interpretedas an average isothermal compression curve. The pump content at 26 hasalmost atmospheric temperature. During the compression 28-30, thistemperature has a tendency to rise adiabatically; On the other hand, theoutside air drawn into the pump may be cooled down ladiabatically belowits initial outside atmospheric temperature while passing through aturbine nozzle. Such refrigerating eiect more than compensates for theadiabatic heating effect during the compression 28--30.

With the second method, the cycle may proceed from in three diierentmanners. By releasing the excess exhaust gas inside the pump to theoutside atmosphere, the total mass of hot gases would expand to a point2l with an amount corresponding to Ztl- 26 left inside the pump and26-2l being pushed out into the open atmosphere. Of course, theexpansive work 25-26-21 would be sacrificed to the outside. From thereon, the cycle proceeds with the portion 20-26 as in the first method.

Another possibility would be to begin cooling without discharge to theoutside. Such procedure however would result in appreciable loss ofsuction intake work 2 6-28-36 The lowest pressure in this case wouldbeabout two-thirds of an atmosphere absolute, as against one-thirdatmosphere absolute with the first method, and correspondingly much lessair could be taken in from the outside.

As a more economical and third possibility applicable in all practicalcases where, within a power plant, a number of pumps. 32 (two or three)are operated in cyclic phase, the first pump is connected after period25 to the next one, thus utilizing the discharge of hot gases Thus thepressure 25 dropsl to'somewhere halfway between 25 and 26, and we maynow sacrifice only a small portion of expansive work of the samecharacter as 25--26-2 1, which is compensated for by a correspondingsaving in compression 20--21--22 in the next pump. These two additionalcyclic functions may readily be handled within the time interval savedduring the more rapid full pressure discharge 24-25.

The working of the cycle so far as the gas weights are concerned may nowbe followed through with reference to Fig, 2. The ordinate at 2D in thisexample indicates that cold gases are present inside the pump to theextent of three units of the weight of hot gas which is to be admittedto the pump as the exhaust of the engine for operating one pump cycle.vAt 22, the same three units are still inside and part of another unitis added as hot exhaust. Beginning from 2| down to 26, the cold gas isdischarged in a linear function. However, from 22 to 24 more hot exhaustgas is added until at 24 it reaches the magnitude of a full unit weight23-24. From there on the exhaust gas weight remains constant whenworking along the best eiiiciency methods while the cold gas contentdecreases to zero, with the result that at the end only the one unit ofexhaust gas remains inside the pump represented by the ordinate 2t`-28.If on the other hand, the pump is operated along the cycle 24-2 5-26,the unit weight of exhaust gas at 24 is still augmented to the total of25--28 at the end of the discharge period. There it is reduced to 265-23by disposing of the excess 25-26 first into the next pump, and the restto the atmosphere.

During the shrinking process from 25-23 in Fig. 1, the weight of gasesinside the pump is not changed and they remain inside during the entireintake process. However, during this intake 28-30 (Fig. 1) outside airis sucked back into the pump until at B it is again iilled up with threeunits of Weight, made up of one unit of cooled exhaust 30-33 identicalto 26-28 (Fig. 2), and two units of fresh intake 30-3I, (Fig. 2) At thispoint the pump is ready to initiate a new cycle of operation beginningat 20.

Thus the working principle of the pump can be summarized in simple termsas follows: one unit of exhaust gas weight is adapted to discharge threeunits of cold gases which may flow by way of a turbine nozzle andturbine wheel, and thereafter to draw back into the pump two other unitsof outside gases until the total intrinsic heat of exhaust gases aboveatmosphere is completely utilized for doing such displacement work. Thusthe breather pump can be interpreted as a thermodynamic transformerwhich utilizes a given weight of hot exhaust gas to move a multipleweight of cold gases through the same pressure differentials. With suchapparatus a very convenient medium for doing work on a turbine wheeloperating at atmospheric temperatures is provid-ed with moderatepressure and speeds of flow, and with relatively large amounts of gasweight. These ultimate objects of the invention are dealt with in detailin my copending application S. N. 240,017 fil-ed concurrently herewithfor Gas turbine system.

Figs. 3 to 9, inclusive, show diagrammatically the cycle of the breatherpump. At the beginning of this cycle, that is at instant 20 in Fig. 1,the pump 32 is filled with cold gases consisting of previous exhaust gascooleddown and fresh air at atmospheric pressure. The exhaust gas cooleddown may be considered as occupying substantially the upper third of thepump above an imaginary dividing line v34 (Fig. 3), with the cold airoccupying the space below the dividing line 34. At this instant an inletvalve 30 for hot exhaust gas, an inlet valve 38 for cold air, and anoutlet valve 40 for cold exhaust gas are all closed, and a cooling unit46 is in its neutral position.

The admission period (Fig. 1) corresponds to the line 20-22--24. Duringthis period the admission valve 36 is kept open as shown in Fig. 4 from20 to 24, and valve 40 stays closed from 2Ii-22 and is open from 22--24.The valve actuating mechanisms are preferably timed from the internalcombustion engine to which the pump is connected; and for the purpose ofunderstanding the invention, the valve mechanisms do not need to bedescribed here. The hot exhaust gases flow into the pump 32, lling upmore and more the upper part of its space. Due to the very hightemperature and very low specic gravity, the hot gases iioat on top ofthe cold original gas content and nally will occupy the upper part ofthe pump space above an imaginary dividing line 42, as shown in Fig. 5.The exact location of stratum 42 depends on the timing of the opening ofvalve 40. During this filling process the cold gases, consisting partlyof previous exhaust gas cooled down and partly of fresh air previouslysucked into the pump 32 (Fig. 3), are compressed into the lower part ofthe pump chamber, with their pressures correspondingly rising. Theexhaust gas which is cooled down may be considered as occupying now thespace between the imaginary dividing line 42 and an imaginary dividingline 44 below which the compressed fresh air lies,'and which isidentical with the imaginary dividing line 34.

through its downward position. The filling process continues until thepressure Within the pump 32 has reached a balance with the gas pressuredesired in a transfer line 50 for the cold gases. The admission line 48is provided with baffles (Fig. 10) and adjacent the entrance to the pumpare additional baiiies.

During the discharge and expansion period 22-24-26 (Figs. 1, 2, 6 and 7the admission valve 35 stays open from 22--24 and is closed from 24--26.The efflux of cold gases begins at 22 by Way of the valve 40 through aline 50 toward, for example, a nozzle box of a turbine such as disclosedin my copending application,`

Serial No. 240,017 filed concurrently herewith for Gas turbine system.The pressure 22-24 stays constant as shown in Fig. 1 if the admittedvolume of exhaust gases covers the volume of the discharged cold gases.Obviously only the cold gas portions contained in the lower half of thepump 32 are affected by this discharge process, and they are the freshair and the previous exhaust gas cooled down. Simultaneously, beginningfrom the point 24, the hot exhaust gas above the imaginary line 42 ofFig. 5 expands until its volume has increased suiciently to ll up thetotal pump space including the lower zones which were occupied formerlyby the cold gases. 'I'he valve 38 is closed all the time 2li-23, valve36 is closed at 24, and valve 40 is also closed at 20. By the time thisprocess is finished, the pressure inside the pump will have dropped toatmospheric, and any further -efiiux ceases at Cooling unit 46 duringthis period is movinguo i so . the process is carried out.

point 28 of Fig. 1.

point 26 with no additional Weights of gas discharged.

During the cooling or condensing period 26,--28-30 (Figs. 1, 2, 8 and 9)the Valve 4D stays closed and the cooling unit 46 is moved into itsuppermost position. A fan 52 (Fig. 10) of the cooling unit 46 begins torotate and produces a rapid circulation of the hot gases through aradiator 54, whereby the hot gases are rapidly cooled. Consequently thegases inside the pump begin to shrink in volume at the rate that heat istaken from them by the Water inside of the cooling unit. The water(Figs. 10,y 11) enters unit 46 through an inlet pipe 56 and exitsthrough an outlet pipe 58. This process may be considered the equivalentof the condensing process in a steam condenser. It will be highlyefcient because the warmer portions of the gases automatically move upinto the upper portions off'the pump, thus admitting to the cooling unit4S just those portions of the gases which are most susceptible to thecooling, while the cold gases iiow to the lower zones of the pump 32.

The shrinking process results in setting up within the pump a partialvacuum down to the The suction valve 38 is then opened and atmosphericair, or a portion of the previous cold gas discharge, is redrawn intothe pump 32, for example by way of a gas turbine, performing anotherlling process until the inside pressure balances again with theatmosphere outside. When the secondary filling process is nished at 30,the lower two-thirds of the pump 32 (Fig. 9) is filled up belowv theimaginary dividing line 34 with the redrawn air or former colddischarge; and the upper one-third of the gases above the imaginary,dividing line 34 is made up of cooled exhaust gas residue. .As theseresidual gases are still somewhat warmer and lighter in Weight than theredrawn cold gases, they will occupy the upper third of the availablespace without substantially any diiusion as Meanwhile, thecoolingapparatus 46 has been rotated down again into its neutralposition (Fig. 3) by suitable mechanism which need not be described forthe understanding of the invention, and the fan 52 has been stopped. Atthis point, the cycle is finished and the new inux of hot gases aspreviously disclosed may start again. The cycle may be repeatedindefinitely.

The foregoing description of the cycle, of

course, merely covers the theoretically desired sequence of cyclicsteps, and discloses how by such operation, a turbine wheel may remaincompletely shielded from hot gases. `Naturally in actual operation thereare unavoidable transfers of heat by radiation'and conduction from thehot gases to the cold gases and consequently -a turbine wheel may bepassed by gas streams of somewhat elevated temperature levels. In orderto obtain best turbine eiiciency it may be even advantageous to operatethe power unit purposely by gases moderately warmer than atmosphericair.

It will be obvious that the breather pump may be operated over only aportion of the complete cycle of Fig. 1. For example the cooling andbreathing portion of the cycle may be used, or this portion of the cyclemaybe omitted and the pump scavenged with air immediately after thedisplacement portion of the cycle is completed.

Figs. and 11 disclose a suitable design of breather pump, and in mycopending application, Serial No. 240,016, filed concurrently herewith,there is disclosed other suitable pump designs. VIn the modication shownin Figs. 10 and 171 the cooling unit 46 is rotatably mounted within thepump and .timed to make one complete revolution during each cycle. It ispreferable to have a variable speed of rotation of the cooler 46 so thatit may pass slowly through its top and bottom positions, or even stop inthese positions, and may move at greater speed between these twopositions.

There are definite reasons for the choice of a location of the coolingunit or recuperator 46 during the several cyclic periods, as shown inFigs. 3,5, 7, and 9. The hot exhaust gases flowing into the pump aresupposed to stay hot during al1 the period 213-22-24-26. Therefore it isdesirable to provide a very eflicient insulation against heat exchangewith the walls, and to have the cooling unit 46 out of direct contactwith the hot gases. On the other hand, the cold gas content of the pumptends to become warmer due to the compression 'from Ztl- 22, and it isthen advantageous to move the cooling unit during that period down intothe cold gases to keep them cool. These requirements are met by thearrangement as shown in Figs. 3 and 5. On the other hand, during thecooling period 26-28, the cooling unit must be in the upper ranges ofits motion In Figs. 10 and 11, fans 52 and 64, are shown. The upper fan52 is needed under all circumstances, whereas the lower fan 64 could bedispensed with. At any rate, the lower fan should cause only a gentlecirculation of the lower strata of the pump content through the coolingsystem. However, the upper fan must be able to circulate the Whole pumpcontent several times a second through the cooling unit in order to keepthe duration of the shrinking period 26--28 down to a small proportionof a pump cycle period. The cooling unit 46 in the pump 32 consists of arecuperator or radiator 54, and fans 52 and 64 positioned respectivelyat the top and bottom of the pump.

Admission and removal of cooling vwater or other cooling fluid to unit46 is eiected respectively through inlet pipe 56 and an outlet pipe 58.These pipes are arranged concentrically and journaled to provide asuitable rotatable shaft mounting for the honeycomb radiator 54.

from the power unit and timed for operation only when the cooling unitis in position in front of The fan 52 will operate therefore when thecooling apparatus 46 is in its upper position, but it will not operatewhen the cooling apparatus 46 is in its lower position although the fan64 will then operate. The fans 52 and 64 may be operated throughsuitable clutches 18 and 80 respectively and bevel gearing 86 and 88.Suitable clutch mechanisms 96 and 92 serve for actuating clutches 18 and60 for throwing the fans in and out of operation. The clutches are timedfrom the prime mover.

The `apparatus for operating the valves, fans and cooling apparatus ofthe pump 32 (Figs. l0 and 11) is driven from a shaft 96 which may beoperated from a prime mover, the exhaust gas from which may be deliveredto the pump. The rotational speed of the main shaft carrying the coolingunit inside the pump, or in other words the relative duration of onepump cycle, depends on the number of pumps making up the power plant andupon the relative ratio of aggregate piston displacement and pumpvolume.

50 The fans 52 and 64 are preferably rotated The shaft 98 is connectedby chains, |00 and |02 running over sprockets |04 and |06 and sprockets|08 and H0, to shafts ||2 and H4, which are in turn connected.- to anddisconnected from shafts ||6 and H8 by the clutches 'i8 and 80,respectively.

The combined inlet pipe and shaft 5S by which the cooling apparatus 46is rotated is actuated from the shaft 9:8 by a chain |20 running over asprocket |22 secured to the shaft 55 and a sprocket |24 which isconnected to the shaft S3 by a clutch |23, which is in turn operated ina predetermined cycle from a cam |28 secured to the shaft 90. The shapeof the cam groove is preferably such that the cooling unit 40 remains inits upper and lower positions for a predetermined portion of the cycle,as has been previously described. A clutch fork |30 serves to operatethe clutch |26 from the cam |28. Shaft 55 is shown as mountedsubstantially coaxially within the pump 32.

The mechanism for operating the valves 36, 33 and 40 comprises an upperjack shaft |32 and a lower jack shaft |34. The upper and lowerjack-shafts |32 and |34 are connected to camshafts |35 and |38,respectively. The valves 38, 38 and 40 are actuated in a predeterminedcycle, as has been previously explained, by rocker arms |40 and |42 fromthe cam shafts |35 and |33. The jack-shafts |32 and |34 are driven fromthe shafts ||2 and ||4 by chains |44 and |40. The clutch mechanisms 30and 92 for throwing in and out of operation the clutches 18 and 80 foroperating the fans, are actuated by cams |48 and |50 mounted on theshafts |32 and |34.

The hot exhaust gases from the cylinders of an internal combustionengine enter the exhaust manifold at rather high velocity against a backpressure which may be in the neighborhood of 2 atmospheres, absolute.Some of the kinetic energy in the gas may be converted to heat byinterposing restrictions in the path of the gas fiow from the exhaustmanifold 48 into the pump 32 past valve 30 (Fig. l0) Perforated platesS0 and 02 respectively, form the upper and lower plates of the pump 32and are located inside of the pump, where they serve to help preventturbulent intermixing of the hot and cold gases.

Circulation of gases through the cooling unit in its upper positionfollows the paths as indicated by numerals 60 and t. The radiator 54 isso arranged that the fan 52 discharges the gases through a housing 'l0into a top opening 'l2 in the radiator. The gases then pass through theradiator 54 and `discharge from side openings 14, l5. The radiator 54has headers |32 which are connected to outlet by pipes 84. A header 04is suitably connected to the inlet 56 bv a pipe 98. The pump 32 isdesigned with a substantially dumbbell section when viewed in sideelevation and a cylindrical or drum section viewed in end elevation towithstand variable pressure `differences from inside to outside. Thesedrum type horizontal pumps are necessarily made heavier than thevertical type of pumps which are described in my aforementionedcopending application, S. N. 240,016.

The pump which has been described may also serve as a pneumaticsupercharger or air compressor. By opening an additional discharge valve52, as shown diagrammatically in Fig. 5, which is connected to anadmission line |54 of an internal combustion power unit, as disclosed inmy aforementioned copending application S. N. 240,017 led concurrentlyherewith, and by keeping on admitting more hot exhaust from 22 wellbeyond 24 to about half Way between 24 and 25, all the cold freshatmospheric air can be delivered in a compressed state to the admissionline |54 and from there into the power unit for supercharging said powerunit. After the valve |52 is closed, the valve 40 may be opened and thedischarge process may continue with a simultaneous expansion of the coldresidue and the hot gases.

The preferred embodiments of the invention herein described are capableof certain modifications without departing from the scope of theinvention to be defined in the following claims.

The invention having been thus described, what is claimed as new is:

l. The method of transferring energy from a body of hot gaseous productsof combustion which comprises, introducing the gas into a chamber andtrapping the gas therein after its pressure has reached substantiallyatmospheric, positively circulating the trapped gas within the chamberand simultaneously circulating a cooling iiuid through the chamber inindirect heat transfer relation with the hot gas to reduce thetemperature of the gas, thereby developing a partial Vacuum within thechamber, and utilizing the vacuum thereby developed to induce influx ofgas into the chamber from an outside source under higher pressure.

2. The method of utilizing the energy in a body of hot fixed gases undersuperatmospheric pressure which comprises, admitting a stream of saidhot gas into a vessel whichis filled with cold gas at substantiallylower pressure, thereby displacing the cold gas and imparting energythereto and forcing the eiiiux of same from the vessel, expanding thehot gas within thevessel to substantially atmospheric pressure, trappingthe hot gas within the chamber, positively circulating the trappedhotgas and simultaneously circulating a cooling fluid through the vesselin indirect heat transfer relation with the hot gas to reduce itstemperature and develop a partial vacuum, and utilizing the vacuumthereby developed to induce iiow of cold gas from an outside sourceunder higher pressure.

3. The method of utilizing the energy content of a body of hot gasesunder superatmospheric pressure which comprises, introducing the hot gasinto the upper part of a vessel lled with cold gas under substantiallyatmospheric pressure, compressing the cold gas into the lower part ofthe vessel by displacement action of the hotl gas while trapping thecold gas against escape from the vessel, circulating a cold fluid inindirect heat transfer relation to the Icold gas undergoing compressionto cool it, discharging the cold gas from the lower part of the vesselunder pressure while expanding the volume of the hot gas to ll thevessel and expanding the hot gas within the vessel to substantiallyatmospheric pressure, and reducing the gas temperature while trappedwithin the vessel, thereby developing a partial vacuum, and utilizingsaid partial vacuum to induce influx of cold gas into the vessel from anoutside source under higher pressure.

4. The method of transferring energy from a body of hot gases undersuperatmospheric pressure to a body of cold gas enclosed in a vessel atsubstantially atmospheric pressure, which comprises introducing aflowing stream of said hot gas into the top of the vessel above and indirect contact with the cold gas, baffling influx of the hot gas Vto thevessel and thereby promoting density stratification of the hot and coldgases Within the vessel as the hot gas displaces the cold gas, utilizingthe energy thereby impartedto the cold gas to force the same from thelower part of the vessel, expanding the hot gas within the vessel downto substantially atmospheric pressure, transferring heat energy retainedby the hot gas to a second body of cold fluid by circulating said iiuid`through the vessel in indirect heat transfer relation with the hot gas,thereby shrinking the gas and developing a partial vacuum Within theves- Isel, and utilizing the vacuum thereby developed to induce flow ofa third body of cold gas from an outside source under higher pressure.

5. The method of compressing and pumping cold gas which comprises,trapping a body of such gas in a vessel at substantially atmosphericpres- 1 sure, introducing hot gas under superatmospheric pressure intothe top of the vessel above and in direct contact with the cold gasthereby displacing the cold gas downwardly while maintaining densitystratification of the ho-t and cold gases,

discharging the compressed cold gas from the lower part of the vessel atsubstantially constant 1 pressure While continuing the introduction ofhot gas thereto, after the cold gas has been removed discharging part ofthe hot gas from the vessel l to expand the retained balance thereof tosubstantially atmospheric pressure, trapping the remaining hot gasWithin the Vessel while cooling it by indirect heat transfer to a bodyof cooling uid circulating through the vessel thereby developing apartial vacuum within the chamber,

and utilizing the vacuum thereby developed to createv influx of gas intothe vessel from an outside source under higher pressure.

6. The method of regenerating energy from a rapidly moving body of hotgas under superatmospheric pressure which comprises converting part ofthe kinetic energy into heat by flowing the gas past flow restrictions,imparting pressure energy of the hot gas to a body of cold gas b-yintroducing the hot gas into a vessel enclosing the cold gas therebydisplacing the cold gas and forcing it out of the vessel While expandingthe hot gas down to substantially atmospheric pressure,

trapping the hot gas within the vessel while transferring heat energytherefrom to a body of cold fluid by circulating said fluid through thevessel in indirect heat transfer relation with the lhot gas, andutilizing the partial vacuum de i veloped by the shrinkage in volume ofthe hot gas to induce ow of a further volume of cold gas into thevessel.

'7. The method of transferring energy from a body of hot gas undersuperatmospheric pressure to a plurality of bodies of cold fluid whichcomprises, trapping one of said bodies of cold fluid l stantiallyconstant pressure and discharging the balance of the cold uid from thevessel at a gradually reducing pressure while allowing the hot gas inthe vessel to displace the cold fluid and expand toatmospheric pressure,trapping the hot gas While circulating a second body of cold fluidthrough the vessel in indirect heat transfer with l the hot gas to lowerthe temperature of the hot gas and thereby shrink its volume and createa partial vacuum Within the vessel, and utilizing the vacuum therebydeveloped to induce influx of a third body of cold fluid into the vesselfrom an outside source under higher pressure.

8. In compressing and pumping cold air, the steps comprising trapping abody of said air in a vessel under substantially atmospheric pressure,introducing into the top of said vessel hot gaseous produr/ts ofcombustion under low superatmospheric pressure, displacing the air inthe upper portion of the vessel with the hot gas and thereby compressingthe air while maintaining density stratification of the air and gaslayers, suspending the introduction of hot gases and discharging thecompressed air from the vessel While expanding the hot gases to ll thevessel, and scavenging the vessel with a new supply of air beforerepeating the cycle,

9. In compressing and pumping cold air, the steps comprising, trapping abody of said air in a vessel under substantially atmospheric pressure,introducing into said vessel at one side thereof a stream of hot gaseousproducts of combustion under low superatmospheric pressure, displacingthe air at that side of the vessel with the hot gas and therebycompressing the air While maintaining stratiiication of the air and gaslayers, continuing the introduction of hot gases in the vessel Whiledischarging the air therefroml under substantially constant pressure,suspending the influx of hot gases and discharging part of the hot gasespreviously introduced to reduce the gas pressure Within the vessel tosubstantially atmospheric, and thereafter scavenging the vessel with afresh supply of air before repeating the cycle.

10. In a gas pump, a chamber having enclosing walls, a va-lved gas inletopening into the top of the chamber, another valved gas inlet and avalved gas outlet ported out in the bottom of the chamber, arecuperative cooling element mounted within the chamber and havingconnections for circulating therethrough a cooling fluid, `and mechanismfor actuating and timing the operations of the valved gas inlets andoutlet.

1l. A'gas pump lcomprising a chamber having a pressure differentialresistant enclosing wall construction, a gas inlet ported lout in oneside of said chamber, a conduit for conducting to said inlet hot gaseousproducts of combustion under pressure, a gas inlet anda gas outletpor-ted out in the opposite side of said chamber, valves for controllingeach of said gas inlets and outlets, means arranged to periodicallydevelop a partial vacuum within said chamber, and actuating and timingmechanism for operating the valves land vacuum developing means.

12. In a fluid pump, a lchamber having an enclosing wall vconstructionadapting it as a pistonless pum-p operable in one cycle both above andbelow atmospheric pressure, a gas inlet ported out in the top of saidchamber, another gas inlet and a gas outlet both ported out in thebottom of said chamber, valves for controlling the operation of each ofsaid gas inlets and gas outlet, a recuperator mounted within saidchamber and having associated therewith means for simultaneouslycirculating a cooling fluid from an outside source and gas from Withinsaid chamber therethrough, and actuating and timing mechanism foroperating `the gas inlet and oultlet control valves and the gascirculating means.

13. Apparatus as defined in claim 10, together with a gas circulatingelement mounted within said chamber and connected in operative relationwith said recuperator cooler.

14. Apparatus as dened in claim 11 in which the chamber element of thepump has a substantially cylindrical cross section viewed in verticalend elevation, and a substantial dumbbell shape viewed in sid-e verticalsection.

15. Apparatus as defined in claim l1 together with baffling elementsdisposed in the path of gas flow into the chamber.

16. Apparatus as defined in claim 10 in which the cooling element ismovably mounted whereby it may be shifted in location Within thechamber.

17. A duid pump .comprising a chamber of substantially cylindrical shapedisposed with its major yaxis horizontal, a gas inlet ported out intothe top of the chamber, a gas inlet and a gas outlet both ported out inthe bottom of the chamber, a recuperator cooling unit rotatably mountedwithin lthe chamber on a horizontal shaft disposed coaxially of thechambers major axis, pipe connections for circulating cooling fluid froman outside source through the cooling elements of .the recuperator,mechanism for circulating gas stored within the chamber through thecooling elements of the recuperator, and actuating and .timing mechanismfor controllably operating said cooling unit, and gas circulatingmechanism.

18. In compressing and pumping cold air, the steps comprising trapping abody of said air in a vessel under substantially latmospheric pressure,introducing into the vessel at one side thereof a stream of hot gaseousproducts of combustion under low superatmospheric pressure, displacingithe air from that side of the vessel with the hot gas and therebycompressing the air by stratification displacement, circulating a coldfluid in indirect heat transfer relation to the air i undergoingcompression to cool the air, discharging the compressed air from theopposite side of the vessel and expanding .the hot gases to fill thevessel, and scavenging the vessel with a new supply of lair lbeforerepeating the cycle.

19. In compressing and pumping cold air, the steps comprising trapping abody of said `air in a vessel -under substantially yatmosphericpressure, introducing into the vessel at one side thereof a stream ofhot gaseous products of `combustion under low superatmospheric pressure,thereby displacing the air yat that side of the vessel with the hot gasand compressing the air by stratification displacement, introducing theflowing gas stream to Ithe vessel in a direction and `at a Velocity suchas to insure against substantial intermixing of the air and gas exceptat their plane of contact, discharging the compressed air from the otherside of the vessel and expanding the hot gases to fill the vessel,developing a partial vacuum Within the vessel, and using said vacuum toscavenge the vessel With a new supply of air before repeating the cycle.

20. In compressing and lpumping .cold gas, the steps comprising trappingya body of said gas in a vessel under substantially atmosphericpressure, introducing into the vessel at one side .thereof a stream ofhot gaseous products -of combustion under low superatmospheric pressure,thereby displacing the cold gas at that side of the vessel with the hotgas and compressing the cold gas, discharging part of the compress-edcold gas from the opposite side of the vessel at substantially constantpressure rand discharging the balance of the cold gas at a graduallyreducing pressure after suspending the introduction of hot gases,expanding the hot gases to ll the vessel and scavenging the vessel witha new supply of cold gas before repeating the cycle.

JOHANN J. WYDLER.

